US7165933B2 - Screw pump for transporting emulsions susceptible to mechanical handling - Google Patents

Screw pump for transporting emulsions susceptible to mechanical handling Download PDF

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Publication number
US7165933B2
US7165933B2 US10/496,255 US49625504A US7165933B2 US 7165933 B2 US7165933 B2 US 7165933B2 US 49625504 A US49625504 A US 49625504A US 7165933 B2 US7165933 B2 US 7165933B2
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United States
Prior art keywords
rotor
emulsion
cylindrical housing
screw
heat
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Expired - Lifetime, expires
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US10/496,255
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English (en)
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US20050008510A1 (en
Inventor
Knud Aage Gerstenberg
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SPX Flow Technology Danmark AS
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KAG Holding AS
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Assigned to KAG HOLDING A/S reassignment KAG HOLDING A/S ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GERSTENBERG, KNUD AAGE
Publication of US20050008510A1 publication Critical patent/US20050008510A1/en
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Assigned to GERSTENBERG SCHRODER A/S reassignment GERSTENBERG SCHRODER A/S ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KAG HOLDING A/S
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • F04D3/02—Axial-flow pumps of screw type

Definitions

  • the invention relates to a screw pump for transport of emulsions susceptible to mechanical handling.
  • the invention relates to a particular design of a screw pump that enables it to transport emulsions, such as emulsions used in the food manufacture, without damaging the emulsions due to the mechanical treatment of the emulsions.
  • Emulsions are mixtures of at least two immiscible phases comprising a continuous phase and one or more discontinuous phases present as small spheres in the continuous phase.
  • the emulsions are composed of an oil/fat phase and a water phase and optionally a gas phase.
  • Emulsions are widely used within food industry in products such as butter, spread, dressings and toppings; as well as within the non-food industry in products such as lotions, cremes and ointments.
  • the properties are to a large extend determined by the size of droplets of the discontinuous phase(s) as well as the distribution. Both the visual appearance as well as properties as viscosity, texture, mouth feel, etc, often referred to as functional properties, is influenced by the size and distribution of the droplets of the discontinuous phase(s).
  • emulsions are composed of at least two immiscible phases there is a risk that an emulsion may break and the two different phases may emerge as visible different components in the product, or that droplets of the discontinuous phase coalesce forming larger droplets with the consequence that the properties of the product changes.
  • Breakdown of an emulsion may appear in different ways depending on the extent of the break down of the emulsion and the properties of the emulsion. Breakdown of the emulsion may appear as streaks having a changed colour in the product, parts of the product having different colour, altered texture of the product or a changed mouth feel of the product. Any of these different appearances of the breaking of the emulsion results in a lower quality product and should therefore be avoided if possible.
  • emulsions are susceptible to influences of physical parameters such as temperature and pressure with the consequence that the visible streaks or areas of the emulsion having changed properties emerge and the product becomes less palatable.
  • U.S. Pat. No. 4,938,660 a screw pump for pumping viscous fluids is described.
  • the pump includes a stator and a rotor lying coaxially with each other and has respective surfaces, which lie seal-tight against each other.
  • WO 99/19630 and WO 99/19631 disclose screw vacuum pumps where the rotors are provided with a cooling system inside the rotors.
  • additives such as emulsifiers are often added to the emulsion, with the consequence that the risk for damaging the emulsion is reduced even though it may not be completely avoided.
  • the object of the present invention is to provide new improved screw pumps for susceptible emulsions, which reduce the risk for damaging a susceptible emulsion during pumping.
  • a screw pump for transporting a viscous product comprising a cylindrical housing ( 1 ) connected to a removable bottom piece ( 2 ) in one end and a removable cap ( 3 ) in the opposite end, a rotor ( 9 ) having one or more screw blades ( 11 ) connected to a driving motor ( 5 ), an inlet ( 7 ) and an outlet ( 8 ), wherein the cylindrical housing ( 1 ) is provided with a jacket ( 4 ) for supply or removal of heat, and the rotor ( 9 ) is provided with means for supply or removal of heat.
  • Such a screw pump according to the invention has shown to be able to transport of a viscous fluid in particular an emulsion in a gentle way without excessive influences of heat or pressure to the product.
  • the screw pump according to the invention is used to transport of emulsions, in particular within the food industry.
  • the design and operation of the screw pump ensures that the pressure of the product entering the pump is essentially maintained throughout the pump. Further the jacket ( 4 ) surrounding the cylindrical housing and the means for supply or removal of heat inside the rotor ( 9 ) ensures that the temperature of the product may be kept within narrow limits during the transport which, combined with the constant pressure, ensures that said susceptible emulsions may be transported in a gentle way using this pump with low risk of damaging the emulsion.
  • the cylindrical housing ( 1 ) is connected to a removable bottom piece ( 2 ) provided with an inlet for the product ( 7 ), and a removable cap ( 3 ) provided with an outlet for the product ( 8 ).
  • the rotor ( 9 ) is connected to the driving motor ( 5 ) via a shaft connected to the bottom piece via a common shaft seal ( 6 ).
  • the rotor ( 9 ) is provided with two screw blades ( 11 ).
  • Surrounding the cylindrical housing ( 1 ) is a jacket ( 4 ) for supply or removal of heat provided with an inlet ( 12 ) and an outlet ( 13 ) for a heat transfer medium.
  • the rotor is provided with an inlet ( 14 ) and an outlet ( 15 ) for a heat transfer medium connected via a channel inside the rotor, indicated in the figure by dashed lines.
  • emulsion according to the invention is to be understood as emulsions in the general understanding of the term.
  • the screw pump according to the present invention is useful for emulsions comprising an oil/fat phase and a water phase and optionally a gas phase.
  • Such emulsions may in relation with transport be regarded as fluids having high viscosities.
  • the emulsions to be used in the pumps according to the invention are emulsions having viscosities higher than 100 cP, preferably higher than 500 cP and most preferred higher than 1000 cP.
  • Such emulsions usually have viscosities that are strongly dependent on the temperature, where the viscosity decreases when the temperature increases.
  • the emulsions often behave as non-Newtonian fluids, i.e., the viscosity is dependent on the shear force being applied to the emulsion.
  • the cylindrical housing ( 1 ) of the pump according to the invention has a circular cross section and a length determined by the distance the emulsion has to be transported. It is important that the inner cross section of the cylindrical housing has same area in the complete length in order to secure that no excessive pressure increase or decrease occur. In some embodiments a small difference between the pressure at the inlet and the outlet of the screw pump may be acceptable. Preferably this difference is a decrease of pressure from the inlet to the outlet of the screw pump.
  • the inner surface of the cylindrical housing has to be smooth in order to avoid deposits of emulsion in irregularities in the surface. Further, such a smooth surface is easier to clean which is advantageous, particularly within the food industry.
  • the inner surface is a highly polished surface, most preferred highly polished steel.
  • the housing may have a length of several meters, such as in the range of 0.2–10 m, preferably 0.5–5 m.
  • the rotor is arranged concentrically in the housing.
  • the means for supply or removal of heat arranged inside the rotor may be any means that is capable of delivering or removing heat from the rotor.
  • Several such means will be known by the person skilled in the art. Examples of such means include electrical heating elements and channels for passage of a heat transfer medium.
  • the means for supply or removal of heat may be provided in only a part of the length of the rotor or it may be extended to the total length of the rotor. More than one means for supply or removal of heat may be provided in a rotor, for example, in different sections of the rotor in order to be able to have different temperatures in different parts of the housing, or means for removal of heat as well as means for supply of heat may be provided.
  • One or more screw blades may be provided on the rotor. Even though there may not be an upper limit for the number of screw blades arranged on the rotor, it is preferred that the number of screw blades is in the range of 1–10, preferably 1–6, and most preferably 2–5. In the case that more than one screw blade is provided, they are preferably placed equidistantly around the rotor, i.e., two screw blades are placed in an angle of 180°, three in an angle of 120°, four in an angle of 90°, etc.
  • the screw blades may be designed in any known shape. It is preferred that the screw blades are formed in a way so that maximal force applied to the product being pumped is applied in the axial direction and minimal force is applied in the radial direction.
  • a foldable screw blade is a preferred example of such a design.
  • Foldable screw blades are designed so that the tangent to the screw line becomes propulsion lines. Usually, only the part of the tangent from the point of contact to one of the points of intersection with the cylindrical housing is used.
  • Such screw blades are further characterised in that they in any position have same inclination with planes perpendicular to the screw axis.
  • the distance between the screw blade(s) and the cylindrical housing is preferably low in order to secure that the amount of material being pumped that is able to escape the pumping between the screw blades and the cylindrical housing is low.
  • the distance between the screw blades and the cylindrical housing may be selected in the range of 0.01 mm and 2 mm, preferably in the range of 0.01 to 1 mm and even more preferred in the range of 0.03 and 0.2 mm.
  • edges of the screw blades function to keep the inner surface of the cylindrical housing free of residual material.
  • edges of the screw blades are made of or provided with a cladding of a hard material, preferably a hard metal.
  • Channels for the product in the screw pump according to the invention is delimited by the inner surface of the housing, the rotor and the screw blade(s). It is essential for the present invention that the area(s) of the cross section of these channels are the same through the length of the screw pump. In this way it is avoided that pressure differences between different sections of the screw pump arise.
  • the height of the channels i.e. the difference between the inner radius of the cylindrical housing and the radius of the rotor is an important factor in determining the rate of heat transfer between the material in the centre of the channel and the heat transfer planes, i.e. the inner surface of the cylindrical housing and the rotor.
  • rate of heat transfer will be higher for a low height compared to a higher height.
  • the person skilled in the art will appreciate that for a fluid having a very high viscosity transport of heat will be slower that for fluids having a lower viscosity.
  • the inner diameter and the diameter of the rotor are preferably selected so that the height of the channels is sufficiently low to secure a suitable heat transfer between the fluid and the heat transfer planes.
  • the ratio of the diameter of the rotor and the diameter of the inner surface of the cylindrical housing may be selected in the range of 0.25 to 0.98. Preferably the ratio is selected in the range of 0.5 to 0.95, more preferred in the range of 0.65 to 0.9.
  • the driving force for the rotor is provided with a motor connected to the rotor via a shaft.
  • a motor connected to the rotor via a shaft.
  • Such motors and shafts as well as bearings, gaskets sealing rings etc. for such a motor and shaft is well known within the area.
  • the motor is an electrical motor.
  • a jacket is provided on the outside of the cylindrical housing in order to supply or remove heat.
  • the jacket may in principle be any type of such jackets known within the area that is able to provide the desired transport of heat.
  • a heat transfer medium is passing through the jacket via an inlet and an outlet.
  • the heat transfer medium may be any suitable medium for transfer of heat. It is preferred that the heat transfer medium is an aqueous medium, preferably water.
  • the heat transfer medium used in the jacket on the cylindrical housing may be the same or a different medium than the medium used in the means for supply of removal of heat provided in the rotor.
  • Screw pumps according to the present invention may, in principle, be used for pumping any emulsion that is susceptible to mechanical or temperature damage.
  • the screw pump is particularly suited for pumping emulsion comprising oil or fat, water, and optionally a gas.
  • the dry matter in said emulsion may be found in the range of 0–90%.
  • emulsions can be mentioned dairy products, butter, margarine, margarine products, spread, mayonnaise, dressings, toppings, dough, creams, lotions, ointments etc.
  • the emulsion is a food.
  • Such emulsions are susceptible to damage by mechanical handling or by exposure to high or low temperatures, particular if such emulsions are manufactured having a low or no content of emulsifiers.
  • Viscosities of the emulsions to be pumped by the screw pump according to the invention is generally higher that 100 cP, preferably higher than 250 cP.
  • the rotational speed of the rotor may be in the range of 10–800 rpm, preferably 25–500 rpm in order to secure a low mechanical burden on the product.
  • the temperature of the product is generally sufficiently high to ensure that the viscosity is suitable to enable pumping of the product, but sufficiently low to avoid damaging the emulsion.
  • the temperature is generally within the range of ⁇ 25 to 85° C., preferably 0 to 50° C., more preferred in the range of 10 to 40° C.
  • the screw pump according to the invention is operated so that the temperature in the proximity of the inner surface of the cylindrical housing is different from the temperature in the proximity of the rotor.
  • the temperature of the jacket may be adjusted to be low in order to obtain a high viscosity reducing the amount of emulsion that escapes between the screw blades and housing, whereas the temperature of the rotor may be adjusted to a higher temperature in order to provide a lower viscosity of the emulsion next to the rotor and thereby facilitate transport of the emulsion.
  • the screw pump is operated so that essentially no pressure gradient is formed between the inlet and the outlet.
  • a screw pump having an inner diameter of the cylindrical housing of 105 mm and a diameter of the rotor of 83 mm was used, provided with a jacket around the cylindrical housing and channels inside the rotor.
  • Heat transfer medium was water for both the jacket and the channels in the rotor.
  • the emulsion was pumped and simultaneously cooled without damaging of the appearance and the functional properties of the emulsion.
  • the emulsion was pumped and simultaneously cooled without damaging of the appearance and the functional properties of the emulsion.
  • the emulsion was pumped and simultaneously cooled without damaging of the appearance and the functional properties of the emulsion.
  • the emulsion was pumped without damaging of the appearance and the functional properties of the emulsion.
  • the emulsion was pumped without damaging of the appearance and the functional properties of the emulsion.
  • the emulsion was pumped without damaging of the appearance and the functional properties of the emulsion.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US10/496,255 2001-12-04 2002-12-02 Screw pump for transporting emulsions susceptible to mechanical handling Expired - Lifetime US7165933B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DKPA200101801 2001-12-04
DKPA200101801 2001-12-04
PCT/DK2002/000808 WO2003048579A2 (en) 2001-12-04 2002-12-02 Screw pump for transporting emulsions susceptible to mechanical handling

Publications (2)

Publication Number Publication Date
US20050008510A1 US20050008510A1 (en) 2005-01-13
US7165933B2 true US7165933B2 (en) 2007-01-23

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Country Status (4)

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US (1) US7165933B2 (de)
EP (1) EP1451471A2 (de)
AU (1) AU2002365681A1 (de)
WO (1) WO2003048579A2 (de)

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US20080093417A1 (en) * 2003-10-10 2008-04-24 Akira Takaguchi Wave Soldering Tank
US8840380B2 (en) 2011-01-21 2014-09-23 Toyota Motor Engineering & Manufacturing North America, Inc. Temperature control ring for vehicle air pump

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JP2004019605A (ja) * 2002-06-19 2004-01-22 Matsushita Electric Ind Co Ltd 流体輸送システム及びその方法
US7074018B2 (en) * 2003-07-10 2006-07-11 Sheldon Chang Direct drive linear flow blood pump
KR100786591B1 (ko) * 2007-02-05 2007-12-21 박승종 전동기 일체형 스크류 펌프
TWI470153B (zh) * 2011-06-28 2015-01-21 Univ Nat Cheng Kung 微型液泵單元、微型液泵模組及電子裝置
CN102400923A (zh) * 2011-12-06 2012-04-04 辽宁省电力有限公司本溪供电公司 由电机驱动的潜水泵
CN102536686B (zh) * 2012-01-10 2014-07-23 三一电气有限责任公司 一种齿轮箱及包括该齿轮箱的风力发电机
CN104495254A (zh) * 2014-11-26 2015-04-08 成都贝发信息技术有限公司 提高药粉冷却速率的药粉输送机
CN104528293B (zh) * 2014-11-26 2017-01-25 成都贝发信息技术有限公司 支持快速生产的风冷式药物输送系统
CN104555299A (zh) * 2014-12-11 2015-04-29 赖卫华 一种快速螺旋输送机
JP2018507762A (ja) * 2015-02-06 2018-03-22 チェン、ジChen, Ji 高周波誘起された加熱を低減するために吸収材料を使用する外部固定器具
CN105545727A (zh) * 2016-02-22 2016-05-04 太仓液压元件有限公司 一种保温单螺杆泵

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GB366541A (en) 1929-11-29 1932-02-05 George Handson Abel Improvements in the manufacture of butter, margarine, and other edible fat products
GB461615A (en) 1935-07-17 1937-02-17 Schou Herbert Improvements in and relating to the production of margarine
US2099937A (en) * 1934-04-09 1937-11-23 Peerless Bread Machinery Corp Apparatus for dough preparation
US2111568A (en) * 1935-02-12 1938-03-22 Lysholm Alf Rotary compressor
FR854061A (fr) 1938-12-07 1940-04-04 Mawen Bielle perfectionnée
US3092017A (en) 1960-08-02 1963-06-04 French Oil Mill Machinery Liquid expressing press
GB1306185A (de) 1970-02-06 1973-02-07
US3720479A (en) * 1971-08-16 1973-03-13 Monsanto Co Devolatilizer rotor assembly
US3795117A (en) 1972-09-01 1974-03-05 Dunham Bush Inc Injection cooling of screw compressors
US4245983A (en) 1978-09-11 1981-01-20 Lindroos Runar Ingvald Screw conveyor for feeding lime sludge or cement to a lime and cement kiln, respectively
GB2076998A (en) 1980-05-30 1981-12-09 Westfalia Separator Ag Control of a butter conveying mechanism
JPS6083556A (ja) 1983-10-15 1985-05-11 Ono Shizumi 油用種実類の飲料製造における酵素失活装置
US4541792A (en) 1983-05-09 1985-09-17 Nrm Corporation Dual loop temperature control system for rubber and other extruders with optional connection for heat pump
US4557103A (en) 1982-09-24 1985-12-10 Sar-A-Lee, Inc. Apparatus for squeeze packaging butter-like products
US4617089A (en) 1982-04-23 1986-10-14 Bayer Aktiengesellschaft Apparatus for discharging high viscosity media in chemical engineering
US4772177A (en) * 1986-06-20 1988-09-20 Hayashi Seiko Co. Ltd. Screw pump
US4793767A (en) * 1985-12-13 1988-12-27 Oy Lars Lundin Patent Ab Device for pumping highly-viscous material, in particular thick oil
US4938660A (en) 1988-06-16 1990-07-03 Andreas Stihl Pump for viscous fluids
US4973708A (en) 1988-10-27 1990-11-27 University Of Kentucky Research Foundation 3-hydroxy-N-methylpyrrolidone and preparation thereof
EP0420191A2 (de) 1989-09-26 1991-04-03 Hayashi Seiko Co., Ltd. Schraubenpumpe
US5028220A (en) 1990-08-13 1991-07-02 Sullair Corpoation Cooling and lubrication system for a vacuum pump
US5281086A (en) 1991-09-11 1994-01-25 Andreas Stihl Pump for viscous fluids
EP0683319A1 (de) 1994-04-20 1995-11-22 ARTEMIS Kautschuk- und Kunststofftechnik GmbH & Cie Exzenterschneckenpumpe
EP0713974A1 (de) 1994-11-25 1996-05-29 Netzsch Mohnopumpen GmbH Exzenterschneckenpumpe
JPH08151113A (ja) 1994-11-28 1996-06-11 Mitsubishi Heavy Ind Ltd スクリュー式冷却器
US5601414A (en) 1995-09-25 1997-02-11 Imo Industries, Inc. Interstage liquid/gas phase detector
US5656286A (en) 1988-03-04 1997-08-12 Noven Pharmaceuticals, Inc. Solubility parameter based drug delivery system and method for altering drug saturation concentration
US5719197A (en) 1988-03-04 1998-02-17 Noven Pharmaceuticals, Inc. Compositions and methods for topical administration of pharmaceutically active agents
WO1998035135A1 (en) 1997-02-07 1998-08-13 J.S. Maskinfabrik A/S Screw conveyor for the transport of liquid substances and/or lumps of materials
EP0891799A1 (de) 1996-04-13 1999-01-20 Bauknecht, Maximillian Verfahren und Anlage zur Entölung fettiger Substanzen
WO1999019630A1 (de) 1997-10-10 1999-04-22 Leybold Vakuum Gmbh Gekühlte schraubenvakuumpumpe
WO1999019631A1 (de) 1997-10-10 1999-04-22 Leybold Vakuum Gmbh Schraubenvakuumpumpe mit rotoren
DE19817351A1 (de) 1998-04-18 1999-10-21 Peter Frieden Schraubenspindel-Vakuumpumpe mit Gaskühlung
US6013140A (en) * 1997-07-28 2000-01-11 Simoneaux; Bret Laser hardening of screw forms
WO2000022301A1 (de) 1998-10-12 2000-04-20 Allweiler Ag Rotor für eine exzenterschneckenpumpe und verfahren zu dessen herstellung
WO2001043559A2 (en) 1999-12-16 2001-06-21 Unilever N.V. Process and equipment for the manufacture of edible spreads
WO2001048383A1 (de) 1999-12-27 2001-07-05 Leybold Vakuum Gmbh Gekühlte schraubenvakuumpumpe
US6394777B2 (en) * 2000-01-07 2002-05-28 The Nash Engineering Company Cooling gas in a rotary screw type pump

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB366541A (en) 1929-11-29 1932-02-05 George Handson Abel Improvements in the manufacture of butter, margarine, and other edible fat products
US2099937A (en) * 1934-04-09 1937-11-23 Peerless Bread Machinery Corp Apparatus for dough preparation
US2111568A (en) * 1935-02-12 1938-03-22 Lysholm Alf Rotary compressor
GB461615A (en) 1935-07-17 1937-02-17 Schou Herbert Improvements in and relating to the production of margarine
FR854061A (fr) 1938-12-07 1940-04-04 Mawen Bielle perfectionnée
US3092017A (en) 1960-08-02 1963-06-04 French Oil Mill Machinery Liquid expressing press
GB1306185A (de) 1970-02-06 1973-02-07
US3720479A (en) * 1971-08-16 1973-03-13 Monsanto Co Devolatilizer rotor assembly
US3795117A (en) 1972-09-01 1974-03-05 Dunham Bush Inc Injection cooling of screw compressors
US4245983A (en) 1978-09-11 1981-01-20 Lindroos Runar Ingvald Screw conveyor for feeding lime sludge or cement to a lime and cement kiln, respectively
GB2076998A (en) 1980-05-30 1981-12-09 Westfalia Separator Ag Control of a butter conveying mechanism
US4617089A (en) 1982-04-23 1986-10-14 Bayer Aktiengesellschaft Apparatus for discharging high viscosity media in chemical engineering
US4557103A (en) 1982-09-24 1985-12-10 Sar-A-Lee, Inc. Apparatus for squeeze packaging butter-like products
US4541792A (en) 1983-05-09 1985-09-17 Nrm Corporation Dual loop temperature control system for rubber and other extruders with optional connection for heat pump
JPS6083556A (ja) 1983-10-15 1985-05-11 Ono Shizumi 油用種実類の飲料製造における酵素失活装置
US4793767A (en) * 1985-12-13 1988-12-27 Oy Lars Lundin Patent Ab Device for pumping highly-viscous material, in particular thick oil
US4772177A (en) * 1986-06-20 1988-09-20 Hayashi Seiko Co. Ltd. Screw pump
US5719197A (en) 1988-03-04 1998-02-17 Noven Pharmaceuticals, Inc. Compositions and methods for topical administration of pharmaceutically active agents
US5656286A (en) 1988-03-04 1997-08-12 Noven Pharmaceuticals, Inc. Solubility parameter based drug delivery system and method for altering drug saturation concentration
US4938660A (en) 1988-06-16 1990-07-03 Andreas Stihl Pump for viscous fluids
US4973708A (en) 1988-10-27 1990-11-27 University Of Kentucky Research Foundation 3-hydroxy-N-methylpyrrolidone and preparation thereof
EP0420191A2 (de) 1989-09-26 1991-04-03 Hayashi Seiko Co., Ltd. Schraubenpumpe
US5028220A (en) 1990-08-13 1991-07-02 Sullair Corpoation Cooling and lubrication system for a vacuum pump
US5281086A (en) 1991-09-11 1994-01-25 Andreas Stihl Pump for viscous fluids
EP0683319A1 (de) 1994-04-20 1995-11-22 ARTEMIS Kautschuk- und Kunststofftechnik GmbH & Cie Exzenterschneckenpumpe
EP0713974A1 (de) 1994-11-25 1996-05-29 Netzsch Mohnopumpen GmbH Exzenterschneckenpumpe
JPH08151113A (ja) 1994-11-28 1996-06-11 Mitsubishi Heavy Ind Ltd スクリュー式冷却器
US5601414A (en) 1995-09-25 1997-02-11 Imo Industries, Inc. Interstage liquid/gas phase detector
EP0891799A1 (de) 1996-04-13 1999-01-20 Bauknecht, Maximillian Verfahren und Anlage zur Entölung fettiger Substanzen
WO1998035135A1 (en) 1997-02-07 1998-08-13 J.S. Maskinfabrik A/S Screw conveyor for the transport of liquid substances and/or lumps of materials
US6013140A (en) * 1997-07-28 2000-01-11 Simoneaux; Bret Laser hardening of screw forms
WO1999019630A1 (de) 1997-10-10 1999-04-22 Leybold Vakuum Gmbh Gekühlte schraubenvakuumpumpe
WO1999019631A1 (de) 1997-10-10 1999-04-22 Leybold Vakuum Gmbh Schraubenvakuumpumpe mit rotoren
DE19817351A1 (de) 1998-04-18 1999-10-21 Peter Frieden Schraubenspindel-Vakuumpumpe mit Gaskühlung
WO2000022301A1 (de) 1998-10-12 2000-04-20 Allweiler Ag Rotor für eine exzenterschneckenpumpe und verfahren zu dessen herstellung
WO2001043559A2 (en) 1999-12-16 2001-06-21 Unilever N.V. Process and equipment for the manufacture of edible spreads
WO2001048383A1 (de) 1999-12-27 2001-07-05 Leybold Vakuum Gmbh Gekühlte schraubenvakuumpumpe
US6394777B2 (en) * 2000-01-07 2002-05-28 The Nash Engineering Company Cooling gas in a rotary screw type pump

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Publication number Priority date Publication date Assignee Title
US20080093417A1 (en) * 2003-10-10 2008-04-24 Akira Takaguchi Wave Soldering Tank
US8215534B2 (en) * 2003-10-10 2012-07-10 Senju Metal Industry Co., Ltd. Wave soldering tank
US9956633B2 (en) * 2003-10-10 2018-05-01 Senju Metal Industry Co., Ltd. Wave soldering tank
US8840380B2 (en) 2011-01-21 2014-09-23 Toyota Motor Engineering & Manufacturing North America, Inc. Temperature control ring for vehicle air pump

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US20050008510A1 (en) 2005-01-13
WO2003048579A3 (en) 2004-04-29
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EP1451471A2 (de) 2004-09-01
AU2002365681A1 (en) 2003-06-17

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